Power transmission



y 1943- F. T. HARRINGTON ET AL 2,324,697

POWER TRANSMISSION I v Filed'oct. 14, 1940 5 Sheds-Shet 1 INVENTORS FERRIS T. HARRINGTON & RALPH L. TWEEDALE ATTORNEY 1943- F. T. HARRINGTON ET AL 2,324,697

' POWER TRANSMISSION Filed Oct. 14, 1940 -5 Sheets-Sheet 2 INVENTORS FERRIS T. HARRINGTON 8- RALPH L. TWEEDALE BY r W z. pm

ATTORNEY FIG. 2

July 20, 194 F. T. HARRINGTON ET AL .7 POWER TRANSMISSION Filed Oct. 14, 1940 ssheets-sne t s I I I I l INVENTORS FERRIS T. HARRINGTON & By RALPH L. TWEEDALE ATTORNEY FIG. 4

U 5 F. T. HARRINGTON sf AL 2,324,697

' l- POWER mungmssmn Filed Oct. 14. i940 s Sheets-Shut s INVENTORS FERRIS T- HARRINGTON -8 RALPH L. TWEEDALE ATTORNEY Patented July 20, 1943 rowan TRANSMISSION l Ferris T. Harrington and Ralph L'Tweedale, De-

troit, Mich., assignors' to Vickers Incorporated, Detroit, Mich, a corporation of Michigan Application October 14, 1940, Serial No. 361,116

' 3 Claims.

This invention relates to power transmissions, particularly to those of the type comprising two or more fluid pressure energy translating devices, one of which may function as a pump and another as a fluid motor.

The invention is more particularly concerned with an improved prefill valve ior use in hydraulic presses and the like.

It has long been.

common in hydraulic presses to economize on power and required pump size-by performing the initial part of the pressing stroke either by gravity or by the use of small booster cylinders having a much less effective area than the main cylinder which is utilized during the final portion of the pressing stroke. A prefill valve accomplishes this by providing an open connection between the, main cylinder and the tank to permit the former to fill with oil during the rapid traverse portion of the stroke. The prefill valve then closes, and pressure liquid is introduced into the main cylinder to build up the final squeeze pressure on the platen. At the conclusion of the pressing stroke when the supply pressure is directed to return the press platen, the prefill valve must again open in order to permit the return of oil from'the main cylinder to the tank, since the effective area of the returning cylinder is ordinarily but a small fraction of the area of the main cylinder.

Considerable difliculty has been experienced with preflll valves in the past, particularly where the reversing control for the press consists of a four-way reverse valve. The latter is ordinarily shifted rather quickly, and shocks are encountered when the pressure in the main cylinder is suddenly relieved, since there is a tremendous amount of potential energy stored in the large volume of oil under compression and in the stressed metal parts of the press.

It is an object of the present invention to pro- -vide an improved prefill valve suitable for use vin a hydraulic press wherein a unitary selfcontainedassembly is provided and incorporates all the mechanism necessary to provide for prefill valve operation and to control the application of pressure fluid to the main ram.

It is also an object to provide such an assembly which may be mounted on various presses in diflerent ways either on the cylinder of the press or on the surge tank thereof or on both and which may be self-supported from its own hydraulic conduit connections.

A further object is to provide a prefill valve which serves to reduce or to eliminate completely any sudden surges or shocks encountered when invention will be apparent from the following.

description, reference being had to the accomthe returning cylinders for the press.

panying drawings wherein apreferred form of the present invention is clearly shown.

In the drawings: t

Figure l is a diagrammatic view of a hydraulicpress circuit incorporating a preierred form of the present invention,

Figure 2 is a longitudinal cross section of an improved pretlll valve constructed in accordance with the present invention.

Figure 3 is a cross section on line 1-3 of Figure 2.

Figure 4 is a cross section on line 4--4 of Figure 3.

Figures 5 through 8, inclusive, are diagrammatic views of the circuit illustrated in Figure 1 showing the flow conditions during various stages of a complete operating cycle.

Referring now to Figure 1, the press is there indicated diagrammatically as comprising a platen l0 having a main ram l2 slidable in a main cylinder l4. Rods I5 connect between the platen l0 and pistons I8 slidable within cylinders 20. The upper ends of the latter form booster cylinders while the lower or smaller ends form Mounted on top of the cylinder 14 is a surge valve 22 which is formed as an angle'valve and connectswith a supply tank 24.

\ A main pump 26, which may be of any suitable fixed or variable displacement, unidirectional delivery type, is driven by an electric motor 28 and withdraws fluid from the tank 24 through a suction conduit 3|]. A delivery conduit 32 extends froin the pump 26 to the pressure port of a pilot-operated, spring-centered, four-way valve 34. The tank ports of the latter are connected to tank by a conduit 36. A suitable reliei valve 38 may be provided in the conduit 32 and is preferably constructed in accordance with the disclosure of the patent to Harry F. Vickers, No. 2,043,453. Valves of this character may beproaided with a venting port for venting the control chamber in order topermit the main valve to inders 20 and also by a branch 42 with an oper ating port 44 of the prefill valve 22. The righthand cylinder port of valve 34 connects by a conduit 46 with a foot valve 48 and by conduit 50 to the lower end of cylinders 20. A branch 52 extends to a second operating port 54 of the prefill valve 22. The foot valve may be constructed'similarly to that shown in the patent to Kenneth'R. Herman, No. 2,200,824, incorporating additionally a check valve and an operating connection for admitting pressure oil to the full area of the bottom of the spool.

The spool of valve 34 is arranged to be shifted under the control of a pilot four-way valve 56, the spool of which is arranged to be shifted by solenoids 58 and 60 as well as by the admission of pilot pressure to operating chambers 62 and 64 in the ends of valve 56. The operating chamber 64 is provided with a free piston 66 of larger diameter than end chamber 82 and having a stroke sufficient to shift the spool of valve 56 from its extreme lefthand position only to its mid position.

The pressure port of valve 56 is supplied with oil from an auxiliary pump 88 driven from the motor 28 and having a customary relief valve 1811:. its delivery-conduit 12. The tank ports of valve 56 are connected to tank by a conduit 14. The cylinder ports of valve 56 connect by conduits 16 and 18 to the pilot operating chambers of the valve 34.

For the purpose of controlling the admission of pressure fluid to the operating chamber 84 and also for controlling the setting of relief valve 38, a solenoid-operated valve 80 is provided. In the position of the valve shown, with the solenoid 82 deenergized, pressure oil is supplied from conduit 12 by a branch conduit 84 having a check valve 86 therein to a conduit 88 leading to the operating chamber 64. In this position the valve 80 also connects a conduit 90 leading to the venting port of the valve 38 with the tank by a conduit 92. When the solenoid 82 is energized, the valve shifts to the right to connect conduit 88 with the tank conduit 92 and to connect together' conduits 84 and 90.

The preflll valve 22 is provided with a pressure take-off port 94 to which a conduit 98 is connected. The port 94 is always in communication with the main cylinder I4. The conduit 96 leads to a pressure responsive relief valve 98, the discharge port of which is connected by a conduit I with the operating chamber 82 of valve 56. A check valve I02 is connected in parallel with the relief valve 98 to form a free path for oil returning from the chamber 82. A tank return line I04 connects with the drain port of valve 98 and also with a similar drain port provided at the valve 22. The conduit 96 has a branch I06 leading to the foot valve 48 for the purpose of opening the same wide whenever pressure exists in the main cylinder I4.

Referring now to Figures 2 through 4, the internal construction of the preflll valve 22 is there illustrated. The main valve comprises an angle body I08 having a flange IIO for mounting by suitable bolts on the main cylinder I4. Alternatively, the flange IIO may carry a pipe flange II2 shown in dotted lines whereby the valve may be connected to the main cylinder by a pipe connection when thevalve is not supported by the main cylinder. The flange H0 is provided with a main cylinder port II4. At right angles to the flange IIO there is provided a flange II6 which forms a tank port H8 and which may be secured to the tank by suitable bolts, not shown, or may carry a pipe flange I20 for connection to a suitable pipe leading to the tank. Both the flanges H0 and H6 are made with sufficient strength to provide support for the full weight of the valve from either flange. Thus the valve may be mounted directly on the cylinder and connected by a pipe to the tank or may be mounted directly on the tank and connected by a pipe to the cylinder. Alternatively, in cases where the tank is mounted directly on top of the cylinder, the valve may be mounted inside of the tank, and the flange IIO bolted directly to the bottom of the tank in which a perforation is provided in register with the port II4. such cases port II8 opens directly into the body of oil in the tank.

Coaxial with the port II8 there are provided two bores I2I and I22 in which is slidable a tubular valve element I24 which forms the main preflll valve. The sleeve I24 is provided with three or more projections I26 at its righthand end forming guiding supports for the sleeve in the bore I2 I when the sleeve is fully retracted to the left.

For the purpose of shifting the sleeve I24, an operating mechanism is provided comprising a body member I28 bolted to the member I08 in alignment with bore I22 at the lefthand end thereof. The member I28 is provided with a main operating cylinder I30 having three annular recesses I32, I34 and I36 disposed along its length. Slidablymounted in the cylinder I30 is a differential-area piston I38. the rod I of which projects through the end wall of the cylinder I30 and is connected to the sleeve I24 by a pin connection I42. The lefthand end of piston I38 carries a tell-tale rod I44 which projects to the outside of the member I28 through a packed opening.

Referring now to Figure 3, the operating port 44 connects to the pressure chamber I48 of a pilot-operated balanced relief valve I48 of the type shown in the previously mentioned Vickers patent. Its control chamber I50 is connected with a pilot relief valve I52 which exhausts through a port I54 to the tank return line I04. The relief valve I48 is thus externally drained in lieu of being drained through a central passage down through the bottom of the valve member. The exhaust port I58 of the valve I48 leads to a check valve I58, the outlet side of which communicates with the recess I32. The valve I48 thus acts as a pressure responsive valve to close communication between port 44 and recess I32 until the pressure in chamber I48 builds up to a predetermined value depending upon the setting of the spring-loaded valve I52. Check valve I58, of course, permits flow through the valve I48 in one direction only.

As a bypass around the valve I48 there is provideda conduit I60 having a check valve I82 opening in the direction opposite to that of check valve I58. The conduit I60 is also provided with a resistance plug I64 forming a restricted path for flow out of the righthand end of bore I30 to the port 44. The plug I64 may be interchanged with plugs of different resistance by removing conduit 42 from port 44 for access to the plug.

Referring now again to Figure 2, the port I84 is connected by an angle passage I66 formed in the members I28 and I08 with the main cylinder port II4. A branch passage I68 having a restrictor plug I10 therein connects between port I32 and port I34. The plug H0 is preferably arranged to be interchangeable with plugs of different resistance by removing the closed plug I12 at the left-hand end of passage I68.

Referring now to Figure 4, the port 54 connects by a passage I14 with the outlet side of a check valve I16. The passage I14 also communicates by an interchangeable restrictor plug I18 and a passage I with a passage I 82 leading to the port I36. The check valve I16 thus permits free flow from the righthand end of cylinder I30 (in Figure 2) to the port 54 while the restrictor I18 permits only a restricted flow in the opposite direction.

With the parts in the position illustrated in Figure 1, in which preflll valve 22 is open from the tank to the main cylinder I4, the delivery of pump 26 is bypassed through the open relief valve 38 which in turn has its control chamber vented to tank through conduit 98, valve 88 and conduit 92. Thus no pressure is supplied to the I main circuit 48-46.

In order to start an automatic cycle of pressing operation, the solenoids 68 and 82 must be energized. For this purpose an electrical control 'circuit consisting of a two-circuit, momentarycontact, starting switch I84 may be provided for closing a circuit extending from line L by a conductor I86 to the solenoid 82 and a second circuit extending from line L by a conductor I88 'to the solenoid 68. The opposite sides of all arranged to be opened when the platen I8 is at the upper limit of its stroke.

It will be seen that, when the starting switch I84 is depressed, solenoids 68 and 82 are energized, and as soon as the platen I8 starts downwardly, switch I94 is closed to hold. the solenoid 82 energized, After this has occurred, the switch I84 may be released, thus deenergizing solenoid 68 without, however, shifting the valve 56. An emergency return switch I96 is arranged when closed to connect line L with a conductor I98 leading to the solenoid 58.

When the solenoids 68 and 82 have been energized by closure of the starting switch I84, the spool of valves 56 and 88 shift to the right to establish flow conditions as illustrated in Figure 5. The vent of valve 38 is closed by the valve 88 and connected to the supply line I2 from pump 68. Check valve 86 is, effective to prevent flow from conduit 98 to conduit I2, however, in the event that the auxiliary pump pressure is lower than the pressure in delivery conduit 32. 4 Shifting of valve 88 also connected operating chamber 64 of valve 56 to tank through conduits 88 and 92.

The shifting of valve 56 admits pressure oil from conduit 12 to conduit I6, thus shifting the main. four-way valve 34 to the right and admitting. pressure oil from conduit 32 to conduit 48 and the booster cylinders 28. This pressure is also applied to the prefill'valve operating mech anism at port 44 but is prevented from reaching the recess I32 by the valve I48 and the check valve I62. The press platen I8 accordingly moves downwardly under the pressure applied to the booster cylinders, and themain ram fills from the tank 24 through the preflll valve. Oil discharged from the return cylinders passes through conduit 58, and, after building up suf- Figure 6. .Pressure oil is accordingly admitted through chamber I56 and check valve I58 to the recess I32 where it acts on the lefthand end of piston I38 in Figure 2. The latter accordingly shifts to the right closing the prefill valve I24 and at .the same time opening a connection between recesses I32 and I34. Pressure 011 which was formerly directed only to the booster cylinders is now directed also to the main cylinder through passage I66 and port II4. Thus the pressing stroke is completed utilizing the full area of the main cylinder plus that of the booster cylinders. In addition, to further increase the tonnage of the press, the pressure in main cylinder I4 is directed from port 94 through conduit I86 tothe foot valve 48 where it reacts over the full spool area at the lower end thereof to open the valve wide and impose no resistance to oil returning from the return cylinders.

When the pressureon the main ram is built up to the setting of the relief valve 98, the latter opens admitting oil through conduits 96and I88 to the operating chamber 62 at the righthand end of valve 56. It being remembered that solenoid 68 was deenergized as soon as the starting switch was released, it will be seen that this pressure oil shifts the spool of valve 56 to its extreme left-.

resent a considerable amount of stored energy which must be relieved before the return movement of the press can begin. This energy is relieved by bleeding the pressure oil from cylinder I4 through port II4, passage I66, recesses I34 and I32, check valve I62, passage I68, restrictor I64, chamber I46, port 44, and conduits 42 and 48 to the lefthand cylinder port of valve 34. The latter having been shifted to its 'extreme lefthand position by the shifting of pilot valve 56, the lefthand cylinder port is now connected to tank through conduit 36.

While this stored energy is being thu relieved, the main prefill valve I24 is stationary; This is due to the fact that the pressure oil applied from conduit 32 through valve 34 and conduits 46 and 58 to the returning ram and through conduit 52, port 54, passage I14, restrictor I18, and passages I88 and I82 to the recess I36 acts on the small areaof piston I38. Opposing this pressure is the pressure in the main cylinder acting on the lefthand face of piston I38 which i several times larger. Accordingly, until the pressure in the main cylinder falls to a predetermined fraction of the pressure built up in the returning cylinders, the valve I24 remains stationary. When this point is reached, however, the piston I38 will be shifted to the left thus again opening the connection between main cylinder I4 and tank 24. These conditions are illustrated in Figure 8.

The press accordingly returns upwardly until the limit switch I94 is again opened which deenergizes the solenoid 82. The spool of valve 88 sition in the same manner as is done by admission of pressure oil to chamber 62.

A feature of the present valve lies in the provision of passage I68 and restrictor IIIl which insure that the valve sleeve I24 remains fully open during [the initial part of the pressing stroke. Should there be leakage past valves I48 or I62 at any normally possible rate, it is free to pass out through restrictor IIll so that a gradual shifting of piston I38 to the right is avoided. In addition there is usually a slight suction in the main cylinder during the preflll stroke due to the resistance which valve I24 imposes to the large volume of flow taking place therethrough. This suction is transmitted through restrictor III] to act on the left face of pistonl38 and thus assists in maintaining the prefill valve open. At this time, of course, the back pressure created by foot valve 48 in lines 50 and 52 is transmitted to the righthand face of piston I38 but this area is rather small, so that the suction acting on the left face materially aids in keeping the valve wide open during the prefill stroke.

Another feature of the present valve resides in its adaptability to a wide variety of press designs and press operating cycles. In applying the valve to some types of presses it is found desirable to utilize a lower pressure in the main ram during the main pressing stroke than exists in the booster rams during the prefill part of the stroke. The provision of the relief valve 98 communicating through port 94 and conduit 96 directly with the main ram cylinder permits such operation by adjusting the relief valve 98 to open at a lower pressure than the sequence valve I48 is set to open at. In cases where the automatic reversal of the press by pressure build-up on the main ram is not desired, the conduit I may then be connected directly to tank instead of to the end chamber 62 of the reverse valve 56.

Another possible use of the present valve with a different type of press concerns its use with hot plate or other curing presses where it is necessary to maintain pressure on the ram for a considerable period after the press has closed. In such instances, the check valve I58 may be moved from the position illustrated in Figure 3 to the bore indicated at 200 in Figure 2. This then acts as a safety check valve to hold pressure in the main ram in the event of loss of pressure in the pump line due to power failure or other derangement. Such a modification, of course, eliminates the delayed opening of the valve I20. at reversal, and for this purpose the righthand end of the sleeve I24 may be tapered or a few small hole drilled in the same to provide gradual release of the main ram pressure.

While the form of embodiment of the invention as herein disclosed constitutes a preferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claims which follows.

What is claimed is as follows:

1. A preflll valve assembly for hydraulic presses of the type having main, booster and return cylinders, a supply tank, and means for selectively supplying pressure fluid to the booster cylinder or the return cylinder, said assembly comprising a housing having main ports connected respectively with the tank and with the main cylinder, a shiftable valve for selectively openin or closing communication between said ports, a doubleacting differential piston and cylinder for shifting said valve and having its larger area effective to close the valve, a first passage communicating between the booster cylinder and the larger area of said differential cylinder, a second passage communicating between the return cylinder and the smaller area of said differential cylinder, 9. pressure responsive valve in the first passage for preventing admission of fluid to the larger area of said differential cylinder until a predetermined pressure has built up on the booster cylinder, a restricted bypass directly around said pressure responsive valve, said bypass including a check valve opening away from the larger area of said differential cylinder, and means associated with said shiftable valve for opening communication between the booster cylinder and the main cylinder when the valve is closed.

2. A prefill valve assembly for hydraulic presses of the type having main, booster and return cylinders, a supply tank, and means for selectively supplying pressure fluid to the booster cylinder or the return cylinder, said assembly comprising a housing having main ports connected respectively with the tank and with the main cylinder, a shiftable valve for selectively opening or closing communication between said ports, hydraulic means for shifting the valve to closed position, means for shifting the valve to open position, a connection providing separate paths for flow in each direction between said hydraulic means and the booster cylinder, a pressure responsive valve in one path for delaying the closing of the valve until a predetermined pressure is reached at the booster cylinder, and means providing permae nently open restricted communication between 7 said hydraulic means and the main cylinder,

whereby reasonable leakage at said pressure responsive valve is ineffective to shift the valve.

3. A prefill valve assembly for hydraulic presses of the type having main, booster and return cylinders, a supply tank, and means for selectively supplying pressure fluid to the booster cylinder or the return cylinder, said assembly comprising a housing having main ports connected respectively with the tank and with the main cylinder, a shiftable valve for selectively opening or closing communication between said'ports, adoubleacting piston and cylinder for shifting said valve, a first passage communicating between, the booster cylinder and the valve-closing side of said piston, a second passage communicating between the return cylinder and the valve-opening side 'of the piston, means including a port opened when the valve is closed for placing the main cylinder in communication with the booster cylinder and the valve-closing side of the piston, a pressure responsive valve in the first passage for preventing admission of fluid to the valve-closing side of said piston until a predetermined pressure has built up on the booster cylinder, and a restricted bypass directly around said pressure responsive valve, said bypass includin a check valve opening out of the valve-closing side of said piston and forming, at the time of reversal of the press, a means for relieving compressed liquid. in the main cylinder whereby, until such liquid is substantially relieved, the valve-closing side of the piston will be exposed to main cylinder pressure and the prefill valve will be prevented from opening.

FERRIS T. HARRINGTON. RALPH L. TWEEDALE. 

